Means for producing compound motion



Aug. 29,l 1939. E. F. COLE .MEANS FOR PRODUCING COMPOUND MOTION Fi1ed`Aug. 5, 1936 3 Sheets-Sheet l I Aug. 29, 1939. E; F, COLE 2,171,355

MEANS' FOR PRODUCING COMPOUND MOTION Filed Aug. 3, 1936 3 Sheets-Sheet 2 v Zzdezz for: 75a fad@ g, m, l CLWQM, /zpdwmu.

All@ 29, 1939 E. F. coLE MEANS FOR PRODUCING COMPOUND MOTION Filed Aug. 3, 1936 3 sheets-sheet 3 Patented Aug. 29, 1939 UNITED STATES PATENT OFFICE MEANS FOR PRODUCING oolvIPoUND MOTION corporation of Indiana Application August 3, 1936, Serial No. 93,943

1 Claim.

The present invention relates to a new and improved method of and means for producing compound motion adapted particularly for utilization in various types and kinds of processing 5 equipment or apparatus requiring a reciprocatory,

Vibratory, sifting or riddling action.

One of the primary objects of the present invention resides in the provision of a novel compound motion having components in a plurality i0 of angularly related planes. I-Ieretofore, devices for actuating processing equipment of the above character have been capable of producing motion only in a single plane. In some instances, the plane of motion has been parallel to the processing surfaces, and in other instances it has been perpendicular thereto. Also, the motion in the perpendicular plane has been either substantially perpendicular or of varying angularity, as for example orbital, relative to the processing surface. In these prior devices, the plane motion, Whether rectilinear or orbital, tends to impart to the material being processed a simple regularity in action which in most instances is disadvantageous and objectionable.l Thus, in the screening and filtering arts, regularity in action contributes towards blinding, and tends to maintain the grouped particles of the material in a constant relative association. When the material is fibrous or grained in character, regularity in action tends to effect an alignment or unidirectional orientation of the particles, and as a result the finished product is likely to be grained and to lack tensile strength in certain directions.V

Also, resistance to compressive forces is defined uni-directionally. By providing a compound motion, regularity in the action on the material, and the attendant disadvantages are effectively avoided.

Another object is to provide a new and irnproved compound motion device comprising two throw elements, such, for example, as eccentrics, which are operable out of phase from a common drive to impart to a processing apparatus two simultaneous components of Vibration in different planes.

A more specific object resides in the provision of a novel compound motion device adapted to actuate a vibrating processing apparatus, and comprising a shaft having two axially spaced eccentrics in diierent angular positions, each eccentric normally acting to impart to the apparatus an orbital motion in a plane perpendicular to the shaft, and the two eccentrics by reason of their staggered relation coaoting to impart to the apparatus a gyratory motion, whereby a Vibratory motion in a plane parallel to the shaft is also obtained.

Another object is to provide a sectional shaft having relatively rotatably adjustable sections for the eccentrics so that the phase relation of 5 the latter may be adjusted at will.

A further object is to provide a compound motion device of the foregoing character which is balanced, and which more particularly has novel adjustable balance wheels for offsetting or counlo teracting the forces of inertia set up by the eccentrics.

Various general objects reside in the provision of a novel compound motion device which is simple, inexpensive and compact in construction, 15 efficient and reliable in operation, capable of convenient assembly and disassembly, and pro* tected against dust and other foreign matter and the loss of lubrication.

Other objects and advantages will become ap- 20 parent as the description proceeds.

In the accompanying drawings, Figure l is a transverse vertical sectional view of a compound motion device embodying the features of my invention.

Fig. 2 is a sectional view taken along the line 2 2 of Fig. 1, and illustrating one of the balance wheels.

Fig. 3 is a sectional view taken along the line 3-3 of Fig. 1, and illustrating the coupling for 30 the shaft sections.

Fig. 4 is a side elevational View partially in section along line 4-4 of Fig. 1, and illustrating the connection between one of the eccentrics and the processing apparatus. 35

Fig. 5 is a diagrammatic view illustrating the eccentric throw.

Fig. 6 is a longitudinal sectional View of a processing apparatus including the compound motion device.` 40

Referring more particularly to the drawings, the compound motion device therein shown, which constitutes the preferred embodiment of the invention, may be adapted to a Wide variety of mechanical operating mechanisms, and par- 45 ticularly mechanisms having reciprocating, Vibrating, ltering, sifting or riddling actions for the processing of material. The device is Well adapted for and hence illustrated in connection with a vibratory screen which will hereinafter be 50 referred to generally as a processing apparatus.

The particular processing apparatus shown for purposes of illustration (see Figs. 1 and. 6) has upper and lower screen trays 6 mounted in aw rigid frame 1. This frame is suspended inter- 55 mediate its ends in an inclined position and in a normally balanced conditionv from the compound motion device, and within a base or foundation having side and end members 8 and 9. The ends of the frame 'I are resiliently supported by suitable springs I8 seating on flanges II secured to the end members 9. Rotation of the frame 'E in either direction tending to result from the vibratory action is resisted by the springs I8.

The compound or composite motion device comprises a main drive element or shaft I2 which is mounted for rotation in two spaced bearingy assemblies I3 on the opposite side members 8 of the foundation. Keyed to one end of the shaft I2 is a pulley I4 adapted to be connected to a suitable source of power (not shown).

The two bearing assemblies I3 preferably are closely alike in construction. Each assembly comprises a housing I5 which is rigidly mounted on the associated frame member 8,V and which is closed at the ends by suitable flanged plates I8 and I'I-to define a lubricant reservoir or chamber I8 about the shaft I2. An anti-friction bearing of the self-aligning type is enclosed within the chamber I8, and consists of the usual inner and outer race members I9 and 2U with interposed balls 2I to complete the bearing relationship. The inner race member I9 is secured to the shaft I2 for rotation therewith in a fixed axial position between a locating sleeve 22, extending through the inner end plate I6, and a lock nut 23. The outer race member 28 is secured in fixed relation within the housing E5, and located axially by the end plates I5 and I'I. In the case of the left-hand bearing assemblyk i3, butV not in the other assembly, end clearance is provided between the outer race member 28 and the plates I6 and Il to permit accurate alignment when the assembly is made and to prevent binding.

To provide a dust and fluid seal, the bores of the end platesyIS and Il are formed with labyrinth grooves 24 and closely embrace the shaft I2 and sleeve 22 respectively, and the external end faces of the plates are formed with annular oil retaining grooves 25. Two flinger disks 28 are secured respectively to the outer end of the shaft I2 and the sleeve 22 in closely running relation to the end faces of the plates I6 and I'I, and are formed'with annular ribs 21 respectively projecting rotatably into the grooves 25.

Keyed to the shaft I2 closely adjacent the inner ends of the bearing assemblies I2 are two balancevvheels 28 which constitute statically balanced fly wheels, and which are provided with compensating weights 29 adjustable in position relative to the axis of rotation. In the preferred construction, each wheel 28 comprises a hub 38 and a concentric rim 3| integrally connected by a side wall 32 to define an annular space 33 in the outer side face. The balance compensating weight 29 preferably consists of a circular disk 34 which is disposed in the space 33 about the hub and against the'wall 32 for adjustment radially of the shaft I2 into different selected positions of eccentricity. Formed in the weight 29 is a diametrical guide opening or slot 35 with threaded through one end wall of the slot 35 into end bearing engagement in a recess 38 in the inner surface of the rim 3|, affords means for adjusting and locating the weight 29. Extending through a radial slot 39 in the wall 32 and into threaded engagement with the weight 29 is a cap screw 40 for locking the weight in position of adjustment.

The composite motion producing mechanism comprises two self-aligning anti-friction eccentric bearing assemblies 4I and 42 which are mounted on opposite end portions of the shaft l2 immediately adjacent the balance wheels 28, and which are operatively connected to opposite sides of the processing apparatus. More particularly, the bearing assemblies 4I and 42 are mounted on eccentrically disposed portions 43 and 44 of the shaft I2. The eccentricity of these portions determines the extent or degree of motion that willbe imparted to the processing apparatus. To obtain the desired compound motion, the eccentrics 43 and 44 are disposed out of angular phase relation about the shaft I2 so that the respective movements imparted by the assemblies 4I and 42 do not coincide but are also out of phase relation or staggered.

Apart from the difference in phase adjustment, the two bearing assemblies 4I and 42 are alike in construction, and hence a description of the assembly 4I will suiiice for both, corresponding parts of the assembly 42 being identified by the same reference numerals.

In its preferred form, the bearing assembly 4I comprisesY inner and outer race members 45 and 4S of the self-aligning type with anti-friction roller elements 41 interposed therebetween to complete the bearing relationship. The inner race member 45 is secured to the eccentric shaft portion 43 for rotation therewith. Two sleeves 48, with outer peripheral end flanges 49, are also rotatable with the shaft portion 43, and abut against opposite ends of the race member 45 to confine the latter in a fixed axial position. The outer race member 48 is fixed in a non-rotatable bearing housing 50 closed at opposite sides respectively by a plate 5I and an `integral flange 52 closely encircling the sleeves 48.

One of the sleeves 48 engages a peripheral shoulder 53 on the shaft I2, and the other abuts against the* hub 30 of the associated balance wheel 28. It will be evident that, by reason of the successive end engagements between the race member I9, the sleeve. 22, the wheel hub 38, the outermost sleeve 48, the race member 45 and the other sleeve 48, the nut 23 and the shoulder 53 -serve to maintain the assembly 4I and the associated assembly I3 and balance wheel 28 in proper position on the shaft I 2.

The outer race member 46 Vhas a press fit in the housing 58, and in the case of the assembly 4I is spaced at the ends from the plate 5I and flange 52. The resulting clearance permits the outer race member 46Vto properly align itself in assembly. No clearance need be provided in the assembly 42.

To provide a dust and fluid seal, a plurality of annular grooves 54, concentric with the axis of rotation of the shaft I2 are formed in the external side face of the plate 5I, and also in the outer side face of the flange 52. Annular ribs 55 formed on the flanges 49 project rotatably with clearance into the grooves 54.

Except for the portions 43 andv 44, all portions of the shaft I2 are concentric with the axis of rotation, although ofvarious diameters to accommodate construction and v.assembly requirements. V.Rotation of the eccentric portions and operation of the processing apparatus tend to set up forces of inertia which if not counteracted would impair smoothness of operation. These forces of inertia. are offset by properly adjusting the compensating weights 29 in the balance Wheels 28. Normally, the weights 29 are located diametrically opposite the throw of the eccentrics.

To provide means for adjusting the angular phase relation of the eccentrics 43 and 44, the shaft I2 is split midway of its ends, as indicated at 56, and the shaft sections are adapted to be connected for joint rotation selectively in different relative angular positions. Apart from the diiference in angular position and the provision for mounting the pulley I4, the two sections of the shaft I2 are substantially symmetrical or alike in form. The means for adjustably connecting the shaft sections may take various forms, but preferably comprises two peripheral flanges 51 and 58 rigid with the adjacent ends, and formed respectively with two sets of peripherally spaced slots 59 and 60 adapted for registration in any one of a plurality of positions for the insertion of fastening means, such as bolts 6I. In the present instance, there are four equally spaced slots in each set, and theslots 59 and 60 of the two sets are diagonally inclined respectively in opposite directions relative to the intersecting radii.

A plurality of peripherally spaced radial grooves 51a and 58a are formed in the abutting end faces of the flanges 51 and 58. These grooves are tapered inwardly and are complementary in shape so that when in registration they dene conical bores into any one of which a tapered dowel pin (ila may be inserted to hold the parts accurately in indexed position. The grooves are closely spaced and adapted for registration in diierent relative angular positions of the shaft sections, and hence permit a finely graduated index adjustment. The various fastening means are maintained apart at established distances peripherally and at equal radial distances, and hence preserve static balance in the coupling assembly.

From the foregoing, it will be evident that the shaft sections may be securely connected for joint rotation selectively in different relative angular positions. The inclination of the slots 59 and 60 in opposite directions permits a limited range of adjustment without requiring removal of the bolts 6I. Also upon removal of the bolts 6|, the shaft sections may be relatively adjusted into any one of four different positions. Thus, in one position, the eccentric portions 43 and 44 will be substantially in phase. In the next position, one section will be degrees in advance of the other section. In the third position, the two sections will be degrees apart in phase. In the fourth position, the aforesaid other section will be 90 degrees in advance of the aforesaid one section. The character of the composite motion produced by the bearing assemblies 4I and 42 will vary in direction, plane and amplitude in accordance with these different adjustments. Accurate alignment of the shaft sections is maintained under all conditions by a dowel pin 62 having oppositely tapered ends inserted in tapered axial bores 63 in the abutting ends.

The shaft I2, intermediate the assemblies 4I and 42 and including the adjustable coupling just described, is enclosed within a. suitable housing indicated generally at 64. In its preferred form, the housing 64 comprises two aligned tubes 65 about the shaft I2 and rigidly connected, as by welding, respectively tothe adjacent faces of the bearing Vhousings 50. Rigidly fixed about and to the free ends of the tubes 65, as by welding, are two rings 66 each of which is formed with an external peripheral groove 61. Two semicylindrical covers 68 embrace and conform to the rings 66 to provide an enlarged accessible space 69 enclosing the shaft coupling. Preferably, these covers are formed along their inner peripheral margins with arcuate ribs 10 fitting into the grooves 61 to maintain the parts in proper assembly. The ends of the covers 68 are clamped in position about the rings 66 by means of encircling straps 1I which are semi-circular in form and provided respectively with opposed lugs 12 at opposite ends connected by suitable tightening bolts 13.y It will be evident that the foregoing construction aifords convenient access to the shaft coupling to permit angular phase adjustment of the shaft sections whenever desired, and at the same time provides a rigid housing fully enclosing the intermediate portion of the shaft I2.

The eccentric bearing assemblies 4I and 42 are operatively connected to opposite sides of the processing apparatus so as to impart to the latter an oscillatory or vibratory motion in a plane perpendicular to the shaft I2. When the eccentric shaft portions 43 and 44 are in direct phase, the resulting orbital motion, illustrated diagrammatically in Fig. 5, is conned to this plane. When the eccentric shaft portions 43 and 44 are angularly oifset into staggered relation, the rigid assembly, including the outer race members 46, the enclosing housings 59, and the intermediate tubular structure, is subjected to` a gyratory motion about the longitudinal axis of the shaft I2. The rotation of the race members 46 is not confined to planes perpendicular toy the shaft axis. On the contrary, the outer race members 46 are subjected to lateral displacement relative to the inner race members 45 and the roller elements 41. This lateral movement is permitted by the self-aligning character of the bearing assemblies 4I and 42 and the clearances between the grooves 54 and ribs 55.

The motion transmitting means for connecting the two eccentric bearing assemblies 4I and 42 to the processing apparatus preferably are alike in construction, and hence corresponding parts thereof are identified by the same reference numerals. Referring to the assembly 4I, the connecting means in its preferred form comprises a rigid bracket or plate 14 which has a circular opening 15 in its upper end receiving the bearing housing 5D, and which isv rigidly secured about the opening by means of bolts 16 to an outer peripheral mounting flange 11 on the housing. The lower end of the member 14 is connected by one or more members 18 to one side of the screen frame 1. As herein shown, the members 18 consist of a plurality of parallel straps connected at their upper ends by means of bolts 19 to the bracket 14. A transverse spacer bar 80 may be interposed and clamped between the bracket 14 and the straps 18. The lower ends of the straps 18 are secured as by means of bolts 8| to the frame member 8, a longitudinal spacer bar 82 being interposed and clamped therebetween.

It will be understood that the lateral shifting movement of the housings 56, resulting from the twisting or gyratory action, imparts a lateral vibratory motion to the screen frame 1. If desired, the straps 18, or equivalent construction, in the connections to the frame 1, may be made of resilient material, such, `for example, as rubber or spring steel to facilitate the lateral vibration.

It will be evident that I haveV provided a new and improved method of and Vmeans for processing material. In the illustrative embodiment of the invention, the material is supplied to the upper end of the screens. 6, and s subjected to vibration longitudinally and vertically of the screens, whereby it is caused to move downwardly. Simultaneously, the material is subjected to vibration laterally of the path of movement. The gyratory motion has longitudinal and transverse components as well as movements in intermediate directions. As a result, irregularity in action on f the material is obtained, and unidirectional arrangement or alignment of the particles is avoided'.

I claim as my invention:

In a processing apparatus, in combination, a support, spaced bearing assemblies on said support, a shaft journalled in said assemblies and. having axially spaced angularly offset eccentric elements, two self-aligning eccentric bearing assemblies mounted von said eccentric elements and. including outer follower elements, a rigid structure connecting said elements for a gyratory motion having an orbital component in a plane perpendicular to` said shaft and an orbital component" longitudinally of said shaft, a processing surface having a frame, and laterally resilient means connecting said frame adjacent the midpoint of the length of said surface to said structure for actuation thereby.

ELZA F. COLE. 

